WO2021068018A1 - Bielle à longueur réglable comprenant un dispositif d'étanchéité - Google Patents

Bielle à longueur réglable comprenant un dispositif d'étanchéité Download PDF

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Publication number
WO2021068018A1
WO2021068018A1 PCT/AT2020/060359 AT2020060359W WO2021068018A1 WO 2021068018 A1 WO2021068018 A1 WO 2021068018A1 AT 2020060359 W AT2020060359 W AT 2020060359W WO 2021068018 A1 WO2021068018 A1 WO 2021068018A1
Authority
WO
WIPO (PCT)
Prior art keywords
connecting rod
sealing
sealing element
hydraulic
piston
Prior art date
Application number
PCT/AT2020/060359
Other languages
German (de)
English (en)
Inventor
Bernhard HÖDL
Helmut Melde-Tuczai
Original Assignee
Avl List Gmbh
Iwis Motorsysteme Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Avl List Gmbh, Iwis Motorsysteme Gmbh & Co. Kg filed Critical Avl List Gmbh
Publication of WO2021068018A1 publication Critical patent/WO2021068018A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/12—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same mounting or demounting piston rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
    • F16J15/3212—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings with metal springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

Definitions

  • the invention relates to a length-adjustable connecting rod for a reciprocating piston engine, in particular for a reciprocating internal combustion engine, the connecting rod having a hydraulic device by means of which an effective length of the connecting rod can be adjusted, the hydraulic device having at least one hydraulic cylinder and a hydraulic piston arranged displaceably therein, which delimits a working space, having, and wherein the working space is sealed by at least one sealing device.
  • the invention also relates to a reciprocating piston machine with such a length-adjustable connecting rod and a corresponding motor vehicle and a production method for such a length-adjustable connecting rod.
  • Spring elements are generally designed to be arranged together with a sealing element in a radial sealing groove and to support the sealing element.
  • Sealing devices are generally used to seal a sealing gap, a large number of different sealing devices and sealing arrangements being known for the most varied of applications.
  • Spring elements for sealing devices are also generally generally known from the prior art. For example, generic sealing arrangements, sealing devices and spring elements are described in the document US Pat. No. 3,645,543.
  • a compression ratio can be changed in a reciprocating piston engine by means of length-adjustable connecting rods.
  • Length-adjustable connecting rods are basically known from the prior art, in particular hydraulic length-adjustable connecting rods, for example from document WO 2015/055582 A2 or document DE 102012 020 999 A1.
  • An example of a length-adjustable connecting rod is shown in FIG. 1.
  • a first aspect of the invention relates to a length-adjustable connecting rod for a reciprocating piston engine, in particular for a reciprocating internal combustion engine, the connecting rod having a hydraulic device by means of which an effective length of the connecting rod can be adjusted, the hydraulic device having at least one hydraulic cylinder and a hydraulic piston arranged displaceably therein, which has a Working space limited, has.
  • the working space is sealed by at least one sealing device.
  • the sealing device has a sealing element and at least a first and a second spring element.
  • the first spring element exerts a force on a first section, in particular a first sealing lip, of the sealing element in such a way that the first section is pressed against a piston rod of the hydraulic piston
  • the second spring element also exerts a force on a second one Section, in particular a second sealing lip, of the sealing element from that the second section is pressed against a cylinder wall of the hydraulic cylinder.
  • a second aspect of the invention relates to a reciprocating piston machine with at least one length-adjustable connecting rod.
  • a third aspect of the invention relates to a motor vehicle with a reciprocating piston engine.
  • a fourth aspect of the invention relates to a sealing device with a sealing element and at least a first and a second spring element, wherein the first spring element exerts a force on a first section, in particular a first sealing lip, of the sealing element that the first Section can be pressed against a first abutment and the second spring element exerts a force on a second section, in particular a second sealing lip, of the sealing element that the second section can be pressed against a second abutment.
  • a fifth aspect of the invention relates to a manufacturing method for a length-adjustable connecting rod, wherein in a first step at least one assembly tool is attached to a sealing element and in a second step the first spring element or the first sealing ring is inserted into the sealing element on a conical surface of the at least one assembly tool, in particular into a first groove of the sealing element and, in a third step, the second spring element or the second sealing ring is pushed onto a hollow conical surface of the at least one assembly tool against the sealing element, in particular a second groove of the sealing element.
  • a particularly simple assembly of the sealing device on the connecting rod can be achieved.
  • a motor vehicle within the meaning of the invention is a motor-driven vehicle, in particular a land, air or water vehicle.
  • the invention is based in particular on the knowledge that very high pressures of more than 1000 bar, depending on the design and operating point even of more than 2000 bar or 3000 bar, can occur in the working spaces of hydraulically adjustable connecting rods, in particular in reciprocating internal combustion engines. This places particularly high demands on the individual components of a device of such a work space, in particular with regard to dimensional accuracy, strength, service life and chemical resistance and / or corrosion resistance.
  • the sealing devices must withstand dynamic pressure loads.
  • TDC top dead center
  • the inertial force of the reciprocating piston pulls the connecting rod upwards.
  • This phase is created in the work area - in the case of a version with stepped pistons and two work areas in the lower work area - with a short rod even a vacuum.
  • the ignition TDC there is a high pressure load in the working area with a long rod or, in the case of a version with stepped pistons and two working areas, a vacuum is created in the upper working area. The pressure in the work space or work spaces thus fluctuates between a vacuum and a pressure peak value.
  • the invention is now based on the further knowledge that such a load could lead to fatigue failure of a spring.
  • the two spring elements are preferably elements that are completely separate from one another.
  • the first spring element acts towards an axis of the hydraulic device and seals off the working space from the piston rod.
  • the second spring element acts away from an axis of the hydraulic device and creates a seal against the cylinder wall of the hydraulic cylinder.
  • the function of the two sections of the sealing element or the spring elements is preferably independent of one another. More preferably, the Function of the first spring element is not influenced by the function of the second spring element or vice versa.
  • the two spring elements are not braced with one another or with respect to one another, there is less material stress, which leads to less or later fatigue of the material. Furthermore, even if one of the spring elements loses its function, the other spring element can continue to perform its full function.
  • the spring elements essentially follow the shape of the sealing element. This ensures good contact with the sealing element and the piston rod and / or the hydraulic cylinder.
  • the spring elements are arranged offset to one another in the direction of a longitudinal axis of the hydraulic device.
  • the diameter of the spring elements can be made larger while the size of the sealing element remains the same.
  • greater forces can be generated by means of the spring elements.
  • the sealing element has a substantially U-shape in cross section, and the two legs of the U-shape form the first section and the second section.
  • a base of the U-shape is arranged in the direction of that area of the hydraulic piston which has the greatest radial extent.
  • the at least one sealing device is arranged in a recess or sealing groove of the hydraulic piston. This allows a particularly secure fit of the Sealing device can be guaranteed.
  • This recess is preferably arranged on the side of the hydraulic piston facing the cylinder wall of the hydraulic cylinder.
  • a relative position of the spring elements to one another is defined by the sealing element.
  • the spring elements are held in the sealing element. This allows the spring elements to be spaced apart without the spring elements having to be connected directly.
  • the spring elements are designed at least essentially as rings, in particular snap rings, which are interrupted at one point. Such rings are particularly easy to assemble and are particularly suitable as spring elements.
  • the spring elements have metal, in particular spring steel wire, or consist of this.
  • This material is particularly suitable for the spring elements and meets the requirements with regard to the temperature requirements in an internal combustion engine particularly well. However, due to the low tension in the spring elements, other materials can also be used.
  • the sections of the sealing element have at least a first groove or a first cavity and a second groove or a second cavity, the spring elements each being arranged in one of the grooves or one of the cavities.
  • the at least one first groove is arranged on a wall of the first sealing lip that faces the second sealing lip and the second groove is arranged on a wall of the second sealing lip that faces the first sealing lip.
  • the spring elements are preferably held in such a way that they cannot escape from the sections of the sealing element as a result of the acceleration of the connecting rod.
  • the spring elements are designed in such a way that their natural frequency is lower than an operating frequency of the Connecting rods and / or a reciprocating piston machine and / or the connecting rod used as intended in a reciprocating piston machine. This prevents the sealing performance of the sealing device from being impaired by certain operating modes or operating points.
  • the forces are generated at least essentially by elastic expansion of the spring elements. In this way, a particularly good sealing effect of the sealing devices can be achieved.
  • the spring elements are designed or set up in such a way that the sections of the sealing element cannot lift off the piston rod and the cylinder wall during normal operation of the connecting rod and / or a reciprocating piston engine.
  • the spring elements are designed for use to seal the working space with an operating pressure in a range from 1000 bar to 3000 bar, in particular from 1500 bar to 2800 bar. This means that the force that the spring elements generate is so strong that the sealing elements - especially under vacuum - do not lift off. A particularly high sealing performance is achieved in this way.
  • the connecting rod has a first connecting rod part and a second connecting rod part, which can be displaced relative to one another in order to adjust the effective length of the connecting rod, in particular along a longitudinal axis of the connecting rod.
  • the first connecting rod part and the second connecting rod part can be pushed into and apart from one another in particular telescopically in order to adjust the effective length of the connecting rod, the first connecting rod part forming the hydraulic cylinder and the second connecting rod part forming the hydraulic piston.
  • FIG. 1 shows a first embodiment of a length-adjustable connecting rod with a sealing device according to the invention in a longitudinal section
  • FIG. 3 shows an enlarged section of the connecting rod from FIG. 1 in the area of
  • FIG. 4a shows an embodiment of a sealing device of the connecting rod from FIGS. 1 and 3 in the installed state in an enlarged individual representation in cross section
  • FIG. 4b shows the exemplary embodiment of a sealing device of the connecting rod from FIG. 4a in the non-installed, unloaded state
  • Fig. 7 shows an embodiment of an assembly tool for a
  • FIG. 8 shows a flow chart of a manufacturing method.
  • FIG. 1 shows a first exemplary embodiment of a length-adjustable connecting rod 1 according to the invention, which is provided for a reciprocating piston engine, in particular for an internal combustion engine for a passenger vehicle.
  • This exemplary embodiment of a connecting rod 1 comprises a first connecting rod part 1a and a second connecting rod part 1b, which can be moved relative to one another in the direction of a longitudinal axis A of the connecting rod 1.
  • the two connecting rod parts 1a and 1b can preferably be telescoped into one another or apart to change the effective connecting rod length L.
  • the effective connecting rod length L is defined in each case by the distance between an axis of rotation of the connecting rod 1 on the reciprocating piston side and an axis of rotation of the connecting rod 1 on the crankshaft side.
  • the first connecting rod part 1 a comprises a large connecting rod eye 19 with a connecting rod bearing on the crankshaft side for connecting the connecting rod 1 to a not here shown crankshaft, and the second connecting rod part 1b a small connecting rod eye 20 for connecting the connecting rod 1 to a reciprocating piston, also not shown here, of a reciprocating piston engine, also not shown.
  • the first connecting rod part 1a has the smaller connecting rod eye at a piston-side end for connecting the connecting rod 1 to a reciprocating piston of a reciprocating internal combustion engine.
  • the second connecting rod part 1b in this case has the larger connecting rod eye for connecting the connecting rod 1 to the crankshaft of the reciprocating piston engine.
  • a hydraulic device 2 is provided inside a connecting rod shaft of the first connecting rod part 1a, which comprises a hydraulic cylinder 3 formed in the connecting rod shaft and a double-acting hydraulic piston 4.
  • the second connecting rod part 1b has a piston rod 9 on its section facing the first connecting rod part 1a.
  • the piston rod 9 is preferably screwed into the second connecting rod part 1b or clamped to it, as can be seen in the exemplary embodiment shown in FIG. 1.
  • the piston rod 9 can be made in one piece with the second connecting rod part 1b.
  • a hydraulic piston 4 is implemented or connected to it. This hydraulic piston 4 is set up to interact with the hydraulic cylinder 3 and is preferably made in one piece with the piston rod 9 or screwed to it, as indicated in FIG. 1 by a dotted line.
  • the hydraulic piston 4 is displaceable in the hydraulic cylinder 3 along the longitudinal axis A.
  • a movement of the hydraulic piston 4 out of the hydraulic cylinder 3 in the direction of the small connecting rod eye 20 results in an increase in the effective connecting rod length L;
  • a movement of the hydraulic piston 4 in the hydraulic cylinder s in the direction of the large connecting rod eye 19 results in a decrease the effective connecting rod length L. In each case, this results in a change in the compression ratio in an associated reciprocating piston engine.
  • a stop sleeve 17 is provided in the connecting rod shaft. This serves as a stop for the hydraulic piston 4 in the direction of the small connecting rod eye 20. This prevents the second connecting rod part 1b, in particular the hydraulic piston 4, from being pushed completely out of the hydraulic cylinder 3 during a length adjustment, in particular during an upward stroke.
  • the hydraulic piston 4 is shown in a central position in FIG. 1 and divides the hydraulic cylinder 3 into a first working space 5a oriented in the direction of the larger connecting rod eye 19 and into a second working space 5b oriented in the direction of the small connecting rod eye 20.
  • Sealing devices 6a, 6b are provided on the hydraulic piston 4 and are held in their position on the hydraulic piston 4 by securing rings 14, 21.
  • the double-acting hydraulic piston 4 adjoins the first working space 5a and the second working space 5b.
  • the sealing devices 6a, 6b seal the hydraulic piston 4 from the hydraulic cylinder 3 and thus also the working spaces 5a, 5b from one another.
  • Another sealing device 6c seals the second working space 5b in the stop sleeve 17 in the direction of the small connecting rod eye 20 and is held in position with a locking ring 22.
  • the two working spaces 5a, 5b are coupled to a hydraulic supply (not shown here), with an associated control device comprising one or more corresponding control valves being able to control alternating filling and emptying of the two working spaces 5a, 5b to effect a length adjustment.
  • the first working chamber 5a which is lower in FIG. 1, is essentially delimited by the hydraulic cylinder 3 (cylinder wall and base) and the hydraulic piston 4.
  • a radially circumferential sealing gap which by the hydraulic cylinder 3 and the hydraulic piston 4 is formed, adjoins the first working space 5a.
  • the sealing device 6a is designed to seal the sealing gap in the axial direction along the longitudinal axis A with respect to the first working space 5a.
  • the sealing device 6a therefore preferably encloses the entire hydraulic piston 4 or the piston rod 9 and rests in the radial direction both on the hydraulic cylinder 3 and on the hydraulic piston 4, preferably in a sealing manner.
  • the upper, second working space 5b in FIG. 1 is essentially delimited by the hydraulic piston 4, a cylinder wall 10 of the hydraulic cylinder 3 and the stop sleeve 17.
  • a radially circumferential sealing gap which is formed by the hydraulic cylinder 3 and the hydraulic piston 4, adjoins the second working space 5b.
  • the sealing device 6b is designed to seal the sealing gap in the axial direction along the longitudinal axis A, with respect to the second working space 5b.
  • the sealing devices 6a, 6b, 6c preferably enclose the entire hydraulic piston 4 or the piston rod 9 and bear in the radial direction both on the hydraulic cylinder 3 and on the hydraulic piston 4 or the piston rod 9, preferably in a sealing manner.
  • the sealing devices 6a, 6b are preferably arranged in a mirrored manner with respect to a plane perpendicular to the longitudinal axis A of the connecting rod in order to achieve an improved sealing effect with respect to the respective working space 5a, 5b.
  • the third sealing device 6c seals the second working space 5b to the outside or in the direction of the small connecting rod eye 20.
  • This sealing device seals the radial sealing gap formed by the stop sleeve 17 and the piston rod 9 in the axial direction in the direction of the small connecting rod 20, which adjoins the second working chamber 5b at the top in the direction of the small connecting rod eye 20 in relation to the illustration in FIG. 1.
  • This third sealing device 6c can, but does not have to, be designed according to the invention.
  • the sealing device 6 has a sealing element 7 with a spring element 8.
  • the spring element 8 is in this case arranged in an end-side, circumferential recess of the sealing element 7 and designed in the form of a V-shaped spiral spring which is circumferentially embodied in the circumferential direction.
  • the recess of the sealing element is circumferentially bounded by two sealing flanks, radially inwards and outwards.
  • An inner leg of the V-shaped spring element 8 acts on the inner sealing flank of the sealing element 7 and presses it against the hydraulic piston 4.
  • An outer leg of the spring element 8 acts on the outer sealing flank of the sealing element 7 and presses it against the cylinder wall 10 of the hydraulic piston 3 Connecting rod.
  • a support ring 13 is provided which supports the sealing element 7 in the loaded state (not shown here) against the sealing gap to be sealed.
  • FIG. 3 shows an enlarged detail I from FIG. 1 in the area of the sealing device 6a, the following explanations also applying to the sealing devices 6b and 6c, which may be of the same design.
  • the sealing device 6a has a sealing element 7 and is arranged in a circumferential sealing groove 15 provided in the hydraulic piston 4. In the axial direction to the longitudinal axis A from FIG. 1, the sealing device 6a is fixed or protected by means of a securing ring 14.
  • the locking ring 14 is preferably designed as a snap ring.
  • the sealing element 7 is preferably made of NBR (nitrile butadiene rubber; Dt .: acrylonite-butadiene rubber) or Teflon TM (tetra-fluoro-ethylene) and has a first spring element 8a and a second spring element 8b.
  • the sealing element 7 is preferably designed in such a way that it follows the geometry of the sealing groove 15 and preferably essentially completely fills it.
  • the sealing element preferably rests circumferentially, preferably in a sealing manner, on the hydraulic piston 4 or the groove walls of the sealing groove 15 formed by it, as well as on the first connecting rod part 1a or the cylinder wall 10 formed by it.
  • FIG. 4a shows the sealing device 6a of the connecting rod 1 from FIGS. 1 and 3, which is arranged in the sealing groove 15, in a further enlarged representation in cross section.
  • the sealing device 6a comprises the sealing element 7 and a first 8a and a second spring element 8b.
  • the spring elements 8a, 8b are each arranged in a first or second circumferential groove 11a, 11b provided in the assigned section 7a, 7b.
  • a position of the spring elements 8a, 8b, in particular with respect to one another, is preferably defined by the sealing element 7.
  • a support ring 13, which is preferably arranged on the edge of the sealing element 7 facing the sealing gap to be sealed, supports the sealing device 6a or the sealing element 7 against the sealing gap.
  • the notch in which the spring elements 8a, 8b are arranged is preferably open towards an end face of the sealing element 7 and essentially has a U-shape.
  • the notch is delimited radially by two sections 7a, 7b of the sealing element 7.
  • a first section 7a is arranged on the radial inside of the sealing element 7 and a second section 7b is arranged on the radial outside of the sealing element 7.
  • These sections or sealing lips 7a, 7b are designed to act on the hydraulic cylinder 3 or its cylinder wall 10, the hydraulic piston 4 or the piston rod 9 (in Fig 4a not shown).
  • the spring elements 8a, 8b act independently of one another, whereby, in the respective effective direction, reliable pressing of the sealing lips 7a, 7b, and thus a sealing effect, is ensured.
  • the first spring element 8a is arranged on the first section or the first sealing lip 7a of the sealing element 7 and designed to exert a force on the first sealing lip 7a such that the first sealing lip 7a, in particular sealingly, against the piston rod 9 or against a Wall 18 of the groove 15 formed in the hydraulic piston 4 is pressed.
  • the second spring element 8b is arranged on the second sealing lip 7b of the sealing element 7 and is designed to exert a force on the second section 7b in such a way that the second section 7b is pressed, in particular sealingly, against the cylinder wall 10 of the hydraulic cylinder 3. Because the spring elements 8a, 8b are preferably not connected to one another, the spring elements 8a, 8b do not influence one another mechanically and act independently of one another.
  • the inventive design of the sealing device 6a in particular the inventive design of the spring elements 8a, 8b, enables a particularly advantageous sealing effect of the sealing element 7 to be achieved. Due to the separate design of the spring elements 8a, 8b, mechanical loads and stresses occurring during operation of the reciprocating piston machine are not transmitted between the spring elements 8a, 8b and thus a material load on the individual spring elements 8a, 8b is reduced.
  • the first spring element 8a preferably acts towards an axis of the hydraulic device 2 or the connecting rod longitudinal axis A and seals the working space 5a from the hydraulic piston 4.
  • the second spring element 8b acts away from the axis of the hydraulic device 2 or the connecting rod longitudinal axis A and seals against the cylinder wall 10 of the hydraulic cylinder 3 or first connecting rod part 1a. This prevents the sections 7a and 7b from lifting off from the sealing surfaces 4 or 9 and 10, in particular under dynamic load. It is ensured that the sections 7a, 7b are in sealing contact with the sealing surfaces 4 or 9 and 10.
  • the sealing element 7 with its sealing lips 7a, 7b forms a U-shape or a recess in cross section, the first and second grooves 11a and 11b, in each of which a spring element 8a, 8b are arranged, each being arranged on the inside of the recess are.
  • the grooves 11a, 11b are preferably designed in such a way that the spring elements 8a, 8b are firmly fixed, in particular against an operational longitudinal acceleration along the connecting rod axis A. It can be provided that a spring element 8a, 8b are each arranged in a cavity of the associated first or second section 7a, 7b.
  • the sealing element 7 preferably has essentially the shape of a ring with the preferably essentially U-shaped recess on one of its end faces. In the installed state, the end face with the recess preferably points in the direction of a working space 5a, 5b.
  • the sealing lips 7a, 7b preferably have different contours, in particular different lengths, in cross section.
  • a longer section 7a, 7b preferably forms a stop for the securing ring 14.
  • that section 7a, 7b of the sealing element 7 is longer which, in an installed state, is opposite the sealing gap to be sealed by 180 ° in a point-mirrored manner.
  • An edge of the sealing lips 7a, 7b, preferably one facing away from the recess of the end face of the sealing element 7, has a bevel, preferably inclined to an outer side of the sealing element 7, in order to ensure that the outer sides of the sealing element 7 rest flat under the action of the spring elements 8a, 8b to favor.
  • the spring elements 8a, 8b are preferably arranged offset to one another with respect to a longitudinal axis A of the connecting rod.
  • the first spring element 8a which is assigned to the extended sealing lip 7a in the exemplary embodiment shown in FIG. 4a, is arranged closer in the direction of the end face of the sealing element 7 facing the lower working space 5a in order to prevent the sealing lip 7a from being in its end area lifts off the wall 18.
  • FIG. 4b shows the sealing device 6a described in FIG. 4a in the unloaded state.
  • Fig. 5 shows an embodiment of a second spring element 8b
  • Fig. 6 shows an embodiment of a first spring element 8a.
  • the spring elements 8a, 8b are preferably designed as a ring, in particular as a snap ring, preferably with a circumferentially uniform cross section.
  • the spring elements 8a, 8b preferably have a circular cross-section, but can also have a substantially rectangular cross-section, preferably with rounded edges.
  • a spring element 8a, 8b preferably has metal, in particular spring steel, or consists of this.
  • the spring elements 8a, 8b preferably have an opening 12, the opening 12 allowing a temporary change in a diameter of the spring element 8a, 8b, in particular during an installation process of the spring element 8a, 8b in the sealing element 7.
  • the spring elements 8a, 8b are preferably completely separate elements.
  • the spring elements 8a, 8b are at least partially connected to one another and can preferably be separated from one another during assembly or during operation of the connecting rod 1.
  • Such a connection of the spring elements 8a, 8b is preferably designed in the form of a tool or in the form of struts or supports.
  • a production method 100 according to the invention for a sealing device 6 according to the invention for a length-adjustable connecting rod 1 in a first step 101 at least one assembly tool is attached to a sealing element 7.
  • a first spring element 8a is pushed into the sealing element 7, in particular into a first groove 11a of the sealing element 7, on a conical surface 16a of the assembly tool.
  • the second spring element 8b is pushed onto the sealing element 7, in particular a second groove 11b of the sealing element 7, on a hollow conical surface 16b of an assembly tool.
  • the assembly tool is preferably designed in the form of a hollow cone, in particular a hollow truncated cone, whose widest or narrowest contour essentially corresponds to the diameter of the frontal recess of the sealing element 7.
  • a frustoconical assembly tool with the end of its largest diameter is attached to the sealing element 7, in particular on or in the recess which is formed by the sections 7a, 7b.
  • the spring element 8a is placed on the conical surface 16a and shifted in the direction of the sealing element 7, preferably by means of an auxiliary element in the form of a slotted casing which essentially follows the shape of the conical surface 16a.
  • Fig. 7 shows the first spring element 8a during assembly and in the snapped-in state.
  • a hollow truncated cone-shaped assembly tool with the end of its smallest diameter is attached to the sealing element 7, in particular on or in the recess which is formed by the sections 7a and 7b.
  • the spring element 8b is placed on the hollow conical surface 16b and shifted in the direction of the sealing element 7, preferably by means of an auxiliary element in the form of a slotted jacket which essentially follows the shape of the hollow conical surface 16b.
  • Fig. 7 shows the second spring element 8b during assembly and in the snapped-in state.
  • Hydraulic piston 5a, 5b working space, first working space, second working space sealing device a first sealing device b second sealing device c third sealing device sealing element, 8a, 8b spring element, first spring element, second spring element

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Actuator (AREA)
  • Sealing Devices (AREA)

Abstract

L'invention concerne une bielle (1) à longueur réglage conçue pour un moteur à pistons alternatifs, comprenant un dispositif hydraulique (2) pour ajuster une longueur (L) effective de la bielle (1), comportant au moins un cylindre hydraulique (3) et un piston hydraulique (4) agencé de manière mobile dans celui-ci, qui délimite une chambre de travail (5a, 5b), la chambre de travail (5a, 5b) étant étanchéifiée par l'intermédiaire d'au moins un dispositif d'étanchéité (6). Ce dispositif d'étanchéité (6) comprend un élément d'étanchéité (7) et au moins un premier et un deuxième élément ressort (8a, 8b), le premier élément ressort (8a) exerçant une force sur une première partie (7a) de l'élément d'étanchéité (7) de manière que cette première partie (7a) soit serrée contre une tige de piston (9) du piston hydraulique (4) ou contre le piston hydraulique (4), et le deuxième élément ressort (8b) exerçant une force sur une deuxième partie (7b) de l'élément d'étanchéité (7) de manière que la deuxième partie (7b) soit serrée contre une paroi de cylindre (10) du cylindre hydraulique (3). Cette invention concerne en outre un moteur à pistons alternatifs, un véhicule automobile, un dispositif d'étanchéité et un procédé de production.
PCT/AT2020/060359 2019-10-08 2020-10-08 Bielle à longueur réglable comprenant un dispositif d'étanchéité WO2021068018A1 (fr)

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ATA50856/2019 2019-10-08
ATA50856/2019A AT522985B1 (de) 2019-10-08 2019-10-08 Längenverstellbares Pleuel mit einer Dichtungsvorrichtung

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DE102021111383A1 (de) 2021-05-03 2022-11-03 Elringklinger Ag Dichtungsanordnung
US20230109363A1 (en) * 2021-10-05 2023-04-06 Saint-Gobain Performance Plastics Corporation Seals and methods of making and using the same

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US2162104A (en) * 1936-08-05 1939-06-13 Nat Oil Seal Co Fluid seal
US2168818A (en) * 1936-11-27 1939-08-08 Robert S Condon Fluid packing
US3645543A (en) 1970-08-14 1972-02-29 Parker Hannifin Corp Shaft packing assembly
BE1014549A3 (nl) * 2001-12-20 2003-12-02 Saint Gobain Performance Plast Afdichtingselement.
WO2007082111A1 (fr) * 2006-01-05 2007-07-19 Saint-Gobain Performance Plastics Corporation Joint annulaire et pompe comprenant celui-ci
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DE102021111383A1 (de) 2021-05-03 2022-11-03 Elringklinger Ag Dichtungsanordnung
US20230109363A1 (en) * 2021-10-05 2023-04-06 Saint-Gobain Performance Plastics Corporation Seals and methods of making and using the same

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AT522985A1 (de) 2021-04-15

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